CN113865012B - Variable-load adjusting air conditioning system and control method thereof - Google Patents

Variable-load adjusting air conditioning system and control method thereof Download PDF

Info

Publication number
CN113865012B
CN113865012B CN202111265937.8A CN202111265937A CN113865012B CN 113865012 B CN113865012 B CN 113865012B CN 202111265937 A CN202111265937 A CN 202111265937A CN 113865012 B CN113865012 B CN 113865012B
Authority
CN
China
Prior art keywords
heat exchanger
outdoor
pipeline
indoor
communicated
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
CN202111265937.8A
Other languages
Chinese (zh)
Other versions
CN113865012A (en
Inventor
皇甫启捷
吕如兵
徐璐
黄泽清
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Gree Electric Appliances Inc of Zhuhai
Original Assignee
Gree Electric Appliances Inc of Zhuhai
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Gree Electric Appliances Inc of Zhuhai filed Critical Gree Electric Appliances Inc of Zhuhai
Priority to CN202111265937.8A priority Critical patent/CN113865012B/en
Publication of CN113865012A publication Critical patent/CN113865012A/en
Application granted granted Critical
Publication of CN113865012B publication Critical patent/CN113865012B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/41—Defrosting; Preventing freezing
    • F24F11/42—Defrosting; Preventing freezing of outdoor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/46—Improving electric energy efficiency or saving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/64—Electronic processing using pre-stored data
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/65—Electronic processing for selecting an operating mode
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/86—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling compressors within refrigeration or heat pump circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/88—Electrical aspects, e.g. circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/10—Temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/10—Temperature
    • F24F2110/12—Temperature of the outside air

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Signal Processing (AREA)
  • Physics & Mathematics (AREA)
  • Fuzzy Systems (AREA)
  • Mathematical Physics (AREA)
  • Thermal Sciences (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

The present disclosure provides a variable load adjustment air conditioning system and a control method thereof, the variable load adjustment air conditioning system including: the outdoor heat exchanger can be controlled to be opened, and the outdoor third heat exchanger can be controlled to be closed when the load is greater than or equal to a first preset value; when the load is less than or equal to a second preset value, the second outdoor heat exchanger can be controlled to be closed, the third outdoor heat exchanger can be controlled to be opened, and the first preset value is more than or equal to the second preset value. According to the method, a component separation method can be adopted, so that the capacity of the non-azeotropic working medium is adjusted under different working conditions, the energy efficiency of the system is improved, meanwhile, the operating range of the working conditions of the system is widened, the efficient operation under different loads is realized, and the heat exchange efficiency is improved while the capacity of the system is adjusted; the problems that the outdoor unit of the system is frosted under severe working conditions, and the comfort of the indoor environment is reduced when defrosting and defrosting are carried out can be solved.

Description

Variable-load adjusting air conditioning system and control method thereof
Technical Field
The disclosure relates to the technical field of air conditioners, in particular to a variable load adjusting air conditioning system and a control method thereof.
Background
When the non-azeotropic working medium is applied to an air conditioning system, from the perspective of system circulation, the non-azeotropic mixed working medium can approach Lorenz circulation in the heat exchange process due to the temperature slippage and the temperature-enthalpy nonlinear relation in the heat exchange process, so that the circulation efficiency is improved. However, from the perspective of heat exchange, the heat transfer of the non-azeotropic working medium is deteriorated due to mass transfer resistance in the heat exchange process, the heat exchange coefficients of evaporation and condensation are all smaller than those of the pure working medium, and the larger the slippage temperature of the non-azeotropic working medium is, the more obvious the heat exchange performance is deteriorated.
Because the mixed working medium air-conditioning circulation system in the prior art has the technical problems that the heat exchange efficiency is low when the working condition load changes, better heat exchange efficiency cannot be obtained when various working conditions are met, the system operation efficiency is low, various changing working condition loads cannot be met, and the like, the variable-load adjusting air-conditioning system and the control method thereof are researched and designed.
BRIEF SUMMARY OF THE PRESENT DISCLOSURE
Therefore, the technical problem to be solved by the present disclosure is to overcome the defect that the heat exchange efficiency of the mixed working medium air conditioning circulation system is low when the working condition load changes, which results in lower system operation energy efficiency, in the prior art, thereby providing a variable load regulation air conditioning system and a control method thereof.
In order to solve the above problems, the present disclosure provides a variable load adjustment air conditioning system, which includes:
the air-conditioning system comprises a compressor, an outdoor first heat exchanger, an outdoor second heat exchanger, an outdoor third heat exchanger, an indoor first heat exchanger and a gas-liquid separator, wherein the gas-liquid separator comprises a first end, a second end and a third end, the air-conditioning system comprises a first boiling point refrigerant and a second boiling point refrigerant, the boiling point of the first boiling point refrigerant is less than that of the second boiling point refrigerant, one end of the outdoor first heat exchanger can be communicated to an exhaust end or a suction end of the compressor, and the other end of the outdoor first heat exchanger can be communicated to the first end of the gas-liquid separator;
the second end is a gas end, the gas separated from the gas-liquid separator can be communicated with one end of the outdoor second heat exchanger through the second end, the third end is a liquid end, and the liquid separated from the gas-liquid separator can be communicated with one end of the outdoor third heat exchanger through the third end;
the other end of the outdoor second heat exchanger and the other end of the outdoor third heat exchanger can be communicated with one end of the indoor first heat exchanger after being mixed, and the other end of the indoor first heat exchanger can be communicated to a suction end or a discharge end of the compressor;
when the load is larger than or equal to a first preset value, the outdoor second heat exchanger can be controlled to be opened, and the outdoor third heat exchanger can be controlled to be closed; when the load is less than or equal to a second preset value, the second outdoor heat exchanger can be controlled to be closed, the third outdoor heat exchanger can be controlled to be opened, and the first preset value is more than or equal to the second preset value.
In some embodiments, the first end and the third end are both located at the bottom of the gas-liquid separator, and the second end is located above half the height of the gas-liquid separator.
In some embodiments, one end of the outdoor first heat exchanger is communicated to a discharge end or a suction end of the compressor through a first pipeline, the other end is communicated to the first end of the gas-liquid separator through a second pipeline, the second end of the gas-liquid separator is communicated with one end of the outdoor second heat exchanger through a third pipeline, and the third end is communicated with one end of the outdoor third heat exchanger through a fourth pipeline.
In some embodiments, the other end of the outdoor second heat exchanger is communicated to one end of a fifth pipeline, the other end of the outdoor third heat exchanger is communicated to one end of a sixth pipeline, the other end of the fifth pipeline is merged with the other end of the sixth pipeline, the fifth pipeline is provided with a first control valve, and the sixth pipeline is provided with a second control valve;
when the load is larger than or equal to a first preset value, the first control valve is opened by controlling the outdoor second heat exchanger to be opened, and the second control valve is closed by controlling the outdoor third heat exchanger to be closed; when the load is less than or equal to a second preset value, the mode of controlling the outdoor second heat exchanger to be closed is to close the first control valve, and the mode of controlling the outdoor third heat exchanger to be opened is to open the second control valve.
In some embodiments, the indoor heat exchanger further comprises a first throttling device, a seventh pipeline, an eighth pipeline and a ninth pipeline, wherein the fifth pipeline is combined with the sixth pipeline and then communicated to one end of the first throttling device through the seventh pipeline, the other end of the first throttling device is communicated to one end of the indoor first heat exchanger through the eighth pipeline, and the other end of the indoor first heat exchanger is communicated to the suction end or the exhaust end of the compressor through the ninth pipeline.
In some embodiments, the four-way valve further comprises a four-way valve, the four-way valve comprises an E end, an S end, a C end and a D end, the E end is communicated with the ninth pipeline, the S end is communicated with the suction end of the compressor, the C end is communicated with the first pipeline, the D end is communicated with the exhaust end of the compressor, and a first communication state of the four-way valve is: the end E is communicated with the end S, the end C is communicated with the end D, at the moment, the indoor operation is in a refrigerating state, and the second communication state of the four-way valve is as follows: the end E is communicated with the end D, the end S is communicated with the end C, and at the moment, the indoor operation is in a heating state; the four-way valve can be switched between the first communication state and the second communication state.
In some embodiments, the system further comprises a tenth pipeline and an indoor second heat exchanger, wherein one end of the tenth pipeline is communicated with the first pipeline and penetrates into the gas-liquid separator for heat exchange, and the other end of the tenth pipeline is communicated to one end of the indoor second heat exchanger.
In some embodiments, the indoor heat exchanger further comprises an eleventh pipeline and a second throttling device, the other end of the indoor second heat exchanger is communicated to the eighth pipeline through the eleventh pipeline, and the eleventh pipeline is provided with the second throttling device;
or the other end of the indoor second heat exchanger is communicated to one end of the indoor third heat exchanger through an eleventh pipeline, the eleventh pipeline is provided with a second throttling device, and the other end of the indoor third heat exchanger is communicated to the ninth pipeline through a twelfth pipeline.
In some embodiments, the portion of the tubing that extends into the gas-liquid separator through the tenth conduit is fluidly sealed from communication with the interior of the gas-liquid separator; and/or the part of the pipe section, penetrating into the gas-liquid separator, of the tenth pipeline is a serpentine pipe section.
In some embodiments, the air conditioner further comprises a first fan, wherein the first fan can drive the air flow in the chamber to firstly flow through the first indoor heat exchanger and then flow through the second indoor heat exchanger, namely, the second indoor heat exchanger is positioned at the downstream side of the first indoor heat exchanger along the air flow direction.
In some embodiments, when further comprising an indoor third heat exchanger, the first fan is capable of driving an indoor air flow through the indoor first heat exchanger, the indoor third heat exchanger, and the indoor second heat exchanger in sequence.
In some embodiments, further comprising a second fan:
the second fan can drive outdoor airflow to flow through the outdoor second heat exchanger firstly and then flow through the outdoor first heat exchanger, namely the outdoor first heat exchanger is positioned on the downstream side of the outdoor second heat exchanger along the airflow flowing direction; and/or the second fan can drive outdoor airflow to firstly flow through the outdoor third heat exchanger and then flow through the outdoor first heat exchanger, namely the outdoor first heat exchanger is positioned on the downstream side of the outdoor third heat exchanger along the airflow flowing direction.
In some embodiments, the outdoor second heat exchanger and the outdoor third heat exchanger are located in parallel along the airflow flowing direction, that is, the outdoor second heat exchanger and the outdoor third heat exchanger are located in a cross section perpendicular to the airflow flowing direction.
The present disclosure also provides a method of controlling a variable load modulated air conditioning system as set forth in any of the preceding claims, comprising:
detecting the operation mode and the load working condition of the air conditioning system;
judging, namely judging the relation between the load working condition and the first preset value and the second preset value;
a control step, when the air conditioner is operated in a cooling mode: when the load is larger than or equal to a first preset value, the outdoor second heat exchanger is controlled to be opened, and the outdoor third heat exchanger is controlled to be closed; when the load is less than or equal to a second preset value, the outdoor second heat exchanger is controlled to be closed, and the outdoor third heat exchanger is controlled to be opened; when the load is smaller than the second preset value and smaller than the first preset value, the outdoor second heat exchanger is controlled to be opened, and the outdoor third heat exchanger is controlled to be opened; wherein the first preset value is more than or equal to the second preset value.
In some embodiments, when further comprising a first control valve and a second control valve:
in the control step, when the load is larger than or equal to a first preset value, the first control valve is opened, and the second control valve is closed; when the load is less than or equal to a second preset value, closing the first control valve and opening the second control valve; opening the first control valve and opening the second control valve when the second preset value is less than the load and less than the first preset value.
In some embodiments, the detecting step can also detect the outdoor ambient temperature T Outer cover ；
The judging step of judging T Outer cover A relationship with a third preset temperature and a fourth preset temperature;
the control step is that when the third preset temperature is less than or equal to T Outer cover When the temperature is not higher than a fourth preset temperature, controlling the outdoor second heat exchanger and the outdoor third heat exchanger to be communicated; when T is Outer cover And when the temperature is lower than the third preset temperature, controlling the outdoor second heat exchanger and the outdoor third heat exchanger to be alternately communicated.
In some embodiments, when further comprising a first control valve and a second control valve:
in the control step, when the third preset temperature is less than or equal to T Outer cover When the temperature is not higher than a fourth preset temperature, controlling the first control valve and the second control valve to be opened; when T is Outer cover In the case where < the third preset temperature,and controlling the first control valve and the second control valve to be opened alternately.
The variable load regulation air conditioning system and the control method thereof have the following beneficial effects:
the air conditioning system can selectively control specific opening of the outdoor second heat exchanger and the outdoor third heat exchanger according to the size of a load working condition, when the load is large, the outdoor second heat exchanger works, the low-boiling point refrigerant is adopted for evaporation heat exchange, the heat exchange effect can be increased in the refrigeration mode, low-boiling point components circulating in the system are more, the volume refrigerating capacity is large, and the air conditioning system can refrigerate under the condition of large load (such as high indoor temperature); when the load is small, the outdoor third heat exchanger works, the high-boiling-point refrigerant is adopted for evaporation and heat exchange, the circulating high-boiling-point components in the system are more, the volume refrigerating capacity is small, and the refrigeration can be carried out under the condition of small load (such as low indoor temperature); by adopting a component separation method, the capacity adjustment of a non-azeotropic working medium under different working conditions is realized, the operating range of the working conditions of the system is expanded while the energy efficiency of the system is improved, the efficient operation under different loads is realized, the capacity adjustment of the system is realized while the heat exchange efficiency is improved, and the heat exchange performance in the evaporation and condensation heat exchange processes of the system is improved; the problems that an outdoor unit of the system is frosted under severe working conditions, and the comfort of an indoor environment is reduced when defrosting and defrosting are carried out are solved; the reheating technology is adopted, so that the air supply temperature can be effectively increased, and the comfort of air supply is improved.
Drawings
FIG. 1 is a schematic diagram of a non-azeotropic working medium system cycle (refrigeration mode) according to a main embodiment of the present disclosure;
FIG. 2 is a schematic diagram of a non-azeotropic working medium system cycle (heating mode) according to the main embodiment of the present disclosure;
FIG. 3 is a schematic view of a refrigeration mode cycle according to an alternate embodiment of the present disclosure;
FIG. 4 is a schematic view of a heating mode cycle according to an alternative embodiment of the present disclosure;
FIG. 5 is a schematic view of a second refrigeration mode cycle according to an alternate embodiment of the present disclosure;
FIG. 6 is a schematic view of a second heating mode cycle according to an alternative embodiment of the present disclosure.
The reference numerals are represented as:
10. a compressor; 21. an outdoor first heat exchanger; 22. an outdoor second heat exchanger; 23. an outdoor third heat exchanger; 31. a first throttling device; 32. a second throttling device; 41. an indoor first heat exchanger; 42. an indoor second heat exchanger; 43. an indoor third heat exchanger; 51. a gas-liquid separator; 51a, a first end; 51b, a second end; 51c, a third end; 61. a four-way valve; E. an E end; s, an S terminal; C. a C terminal; D. a D terminal; 71. a first control valve; 72. a second control valve; 81. a first fan; 82. a second fan;
101. a first pipeline; 102. a second pipeline; 103. a third pipeline; 104. a fourth pipeline; 105. a fifth pipeline; 106. a sixth pipeline; 107. a seventh pipeline; 108. an eighth pipeline; 109. a ninth conduit; 110. a tenth pipeline; 111. an eleventh line; 112. a twelfth pipeline.
Detailed Description
Primary embodiment, as shown in fig. 1-2, the present disclosure provides a variable load regulating air conditioning system comprising:
the air-conditioning system comprises a compressor 10, an outdoor first heat exchanger 21, an outdoor second heat exchanger 22, an outdoor third heat exchanger 23, an indoor first heat exchanger 41 and a gas-liquid separator 51, wherein the gas-liquid separator 51 comprises a first end 51a, a second end 51b and a third end 51c, the air-conditioning system comprises a first boiling point refrigerant and a second boiling point refrigerant, the boiling point of the first boiling point refrigerant is less than that of the second boiling point refrigerant, one end of the outdoor first heat exchanger 21 can be communicated to a gas discharge end or a gas suction end of the compressor 10, and the other end of the outdoor first heat exchanger 21 can be communicated to the first end 51a of the gas-liquid separator 51;
the second end 51b is a gas end, the gas separated in the gas-liquid separator 51 can be communicated with one end of the outdoor second heat exchanger 22 through the second end 51b, the third end 51c is a liquid end, and the liquid separated in the gas-liquid separator 51 can be communicated with one end of the outdoor third heat exchanger 23 through the third end 51 c;
the other end of the outdoor second heat exchanger 22 and the other end of the outdoor third heat exchanger 23 can be communicated with one end of the indoor first heat exchanger 41 after being mixed, and the other end of the indoor first heat exchanger 41 can be communicated to a suction end or a discharge end of the compressor 10;
when the load is greater than or equal to a first preset value, the outdoor second heat exchanger 22 can be controlled to be opened, and the outdoor third heat exchanger 23 can be controlled to be closed; when the load is less than or equal to a second preset value, the outdoor second heat exchanger 22 can be controlled to be closed, and the outdoor third heat exchanger 23 can be controlled to be opened, wherein the first preset value is more than or equal to the second preset value.
The second end 51b can communicate with one end of the outdoor second heat exchanger 22, and the third end 51c can communicate with one end of the outdoor third heat exchanger 23.
The air conditioning system can select and control specific opening work of the outdoor second heat exchanger and the outdoor third heat exchanger according to the size of a load working condition, when the load is large, the outdoor second heat exchanger works, the low-boiling point refrigerant is adopted for evaporation heat exchange, the heat exchange effect can be improved in the refrigeration mode, low-boiling point components circulating in the system are more, the volume refrigerating capacity is large, and the refrigeration can be carried out under the condition of large load (such as high indoor temperature); when the load is small, the outdoor third heat exchanger works, the high-boiling-point refrigerant is adopted for evaporation and heat exchange, the circulating high-boiling-point components in the system are more, the volume refrigerating capacity is small, and the refrigeration can be carried out under the condition of small load (such as low indoor temperature); by adopting a component separation method, the capacity adjustment of a non-azeotropic working medium under different working conditions is realized, the energy efficiency of the system is improved, the operating range of the working conditions of the system is expanded, the efficient operation under different loads is realized, the capacity adjustment of the system is realized, the heat exchange efficiency is improved, and the heat exchange performance in the evaporation and condensation heat exchange processes of the system is improved; the problems that an outdoor unit of the system is frosted under severe working conditions, and the comfort of an indoor environment is reduced when defrosting and defrosting are carried out are solved; this openly still through adopting the reheat technique, can effectively improve air supply temperature, improve the travelling comfort of air supply.
The method can achieve the purpose of adjusting the system capacity by changing the concentration ratio of the non-azeotropic mixed working medium by utilizing the different characteristics of the non-azeotropic working medium and the different refrigerant volume heating capacity.
Therefore, the present disclosure provides a novel air conditioning system based on the above two points, the system adopts a component separation technology, fully exerts the heat exchange characteristics of the non-azeotropic working medium, reduces the influence of heat transfer deterioration of the non-azeotropic working medium on the system, and simultaneously realizes the change of the operating component concentration of the refrigerant in the system through the switching of the valve, thereby changing the system capacity to adjust the system load, widening the operating condition of the system, and enabling the system to operate near the optimal state point under different operating conditions.
The invention solves the following technical problems:
1. the problem that a conventional mixed working medium air-conditioning system is too low in operation energy efficiency is solved;
2. the problem of low heat exchange efficiency of a conventional mixed working medium circulating system is solved;
3. the problems that the deviation of the running condition of the compressor is large and the energy efficiency of the system is low are solved.
Has the beneficial effects that: the technical effects of this application: the heat exchange characteristic of a non-azeotropic working medium is fully utilized, and the condensation side adopts a segregation mode, so that the influence of non-condensable gas on the heat exchange process in the heat exchange process is reduced, and the heat exchange efficiency is improved; meanwhile, the adopted component separation method also reduces the influence of mass transfer resistance on the heat exchange process in the evaporation process. The concentration of refrigerant circulating components in the system is adjusted through switching the component separation device and the valve, and after high-efficiency operation under different loads is realized, the operation condition of the system is widened, so that the system can operate near an optimal state point under different loads. During heating operation, the temperature slippage characteristic of the non-azeotropic working medium is fully utilized, the defrosting and defrosting effects of the air conditioning unit under severe working conditions are remarkable, and the comfort of the indoor environment of the heating operation is improved.
In the condensation process, the high-boiling point refrigerant is first condensed, so that the proportion of the high-boiling point component in the gas phase is gradually reduced (the proportion of the low-boiling point component is increased), and the proportion of the high-boiling point component in the liquid phase is increased. Therefore, after condensing for a period of time, vapor-liquid separation is carried out, so that the separated liquid refrigerant is mainly high-boiling point working medium, and the separated gaseous refrigerant is mainly low-boiling point working medium.
The system can respectively operate the refrigerants with different components through component separation, and as mentioned above, the physical properties of the refrigerants are different, and the volumetric refrigerating capacities of the refrigerants are different. Therefore, under the same frequency, the system can have different operation capacities, and the frequency conversion technology of the compressor is combined, so that the operation range of the system is widened.
Such as: if the capacity and the load of the system need to be improved, the concentration of low boiling point components in the system can be increased by a component separation method, and the volume refrigerating capacity is increased; if the load of the system is to be reduced, it is necessary to increase the concentration of the high boiling point component in the system.
The improvement of this disclosure lies in:
the air conditioning system is applied to:
1. different from a conventional refrigeration system, the proposal adopts a non-azeotropic refrigerant;
2. by adopting a component separation method, the capacity of the system is adjusted, the heat exchange efficiency is improved, and the heat exchange performance of the evaporation and condensation heat exchange processes of the system is improved.
3. Through the switching of the valve, the adjustment of the volume of the non-azeotropic working medium under different working conditions is realized, the energy efficiency of the system is improved, the operating range of the working conditions of the system is widened, and the high-efficiency operation under different loads is realized.
4. The problem of the system outdoor unit frost under abominable operating mode, indoor environment travelling comfort descends when defrosting changes frost is solved.
5. And the reheating technology is adopted, so that the air supply temperature is increased, and the air supply comfort is improved.
The problem of defrosting and defrosting is solved by sacrificing a small part of heat exchange area. When heating operation, there are 3 heat exchangers outdoor and all as the evaporimeter. The non-azeotropic working medium has the advantages that due to the temperature slip characteristic, the temperature is gradually increased during heat exchange in the evaporator, so that the evaporation temperature of the refrigerant in the small heat exchanger is lower than the dew point temperature of the outdoor working condition, the small outdoor heat exchanger frosts, due to the temperature slip characteristic, the temperature of the refrigerant coming out of the outdoor second heat exchanger 22 is higher than the dew point temperature, then the refrigerant enters the outdoor first heat exchanger 21 for heat exchange, and due to the fact that the temperature of the refrigerant for heat exchange is higher than the dew point temperature and lower than the outdoor dry bulb temperature, the outdoor first heat exchanger cannot frost. When the frost layer of the outdoor second heat exchanger 22 is built up to a certain extent, the second control valve 72 is closed and the first control valve 71 is opened, so that the outdoor third heat exchanger 23 operates in place of the outdoor second heat exchanger 22. So as to realize frosting and defrosting in turn without stopping the machine.
In some embodiments, the first end 51a and the third end 51c are both located at the bottom of the gas-liquid separator 51, and the second end 51b is located above half the height of the gas-liquid separator 51 (the first end, the second end, and the third end are all ends of a pipeline). The third end, the second end and the first end of the gas-liquid separator are preferably arranged, the first end is an inlet end of the gas-liquid separator in a refrigeration mode, fluid (including gas-liquid two phases) condensed by the outdoor first heat exchanger can be effectively introduced through the top of the gas-liquid separator, the second end is a gas outlet end of the gas-liquid separator in the refrigeration mode, and gas at the upper part of the gas separator can be led out above the half height of the gas-liquid separator so as to be led out into the indoor second heat exchanger; the liquid outlet end of the gas-liquid separator can lead the liquid at the bottom of the gas separator to the indoor third heat exchanger when the third end is in a refrigeration mode, so that the gas and liquid after gas-liquid separation can be respectively led out, and low-boiling-point refrigerant heat exchange or high-boiling-point refrigerant heat exchange is realized according to different working condition loads, so that different refrigeration capacities are output, and the heat exchange efficiency is improved.
In some embodiments, one end of the outdoor first heat exchanger 21 is communicated to a discharge end or a suction end of the compressor 10 through a first pipeline 101, the other end is communicated to the first end 51a of the gas-liquid separator 51 through a second pipeline 102, the second end 51b of the gas-liquid separator 51 is communicated with one end of the outdoor second heat exchanger 22 through a third pipeline 103, and the third end 51c is communicated with one end of the outdoor third heat exchanger 23 through a fourth pipeline 104. The first pipeline can guide the compressor exhaust gas to the outdoor first heat exchanger 21 for condensation and heat release in the refrigeration mode, and can guide the refrigerant coming out of the outdoor first heat exchanger back to the air suction end of the compressor in the heating mode; the third pipeline and the fourth pipeline are respectively used for leading out the gas outlet end of the gas separator to the indoor second heat exchanger and leading out the liquid outlet end of the gas separator to the indoor third heat exchanger, so that the gas and liquid after gas-liquid separation are respectively led out, low-boiling-point refrigerant heat exchange or high-boiling-point refrigerant heat exchange is realized according to different working condition loads, different refrigerating capacities are output, and the heat exchange efficiency is improved.
In some embodiments, the other end of the outdoor second heat exchanger 22 is connected to one end of a fifth pipeline 105, the other end of the outdoor third heat exchanger 23 is connected to one end of a sixth pipeline 106, the other end of the fifth pipeline 105 is merged with the other end of the sixth pipeline 106, the fifth pipeline 105 is provided with a first control valve 71, and the sixth pipeline 106 is provided with a second control valve 72;
when the load is larger than or equal to a first preset value, the first control valve 71 is opened by controlling the outdoor second heat exchanger 22 to be opened, and the second control valve 72 is closed by controlling the outdoor third heat exchanger 23 to be closed; when the load is less than or equal to the second preset value, the first control valve 71 is closed in the manner of controlling the outdoor second heat exchanger 22 to be closed, and the second control valve 72 is opened in the manner of controlling the outdoor third heat exchanger 23 to be opened.
The first control valve is arranged on a fifth pipeline communicated with the outdoor second heat exchanger, and the second control valve is arranged on a sixth pipeline communicated with the outdoor third heat exchanger, so that whether the outdoor second heat exchanger and the indoor third heat exchanger are communicated or not can be controlled respectively; when the load is large, the outdoor second heat exchanger works, the low-boiling-point refrigerant is adopted for evaporation heat exchange, the heat exchange effect can be increased in a refrigeration mode, the circulating low-boiling-point components in the system are more, the volume refrigerating capacity is large, and the refrigeration can be carried out under the condition of large load (such as high indoor temperature); when the load is small, the outdoor third heat exchanger works, the high-boiling-point refrigerant is adopted for evaporation and heat exchange, the circulating high-boiling-point components in the system are more, the volume refrigerating capacity is small, and the refrigeration can be carried out under the condition of small load (such as low indoor temperature); by adopting a component separation method, the capacity of non-azeotropic working media under different working conditions is adjusted, the energy efficiency of the system is improved, meanwhile, the operating range of the working conditions of the system is widened, the high-efficiency operation under different loads is realized, the heat exchange efficiency is improved while the capacity adjustment of the system is realized, and the heat exchange performance of the evaporation and condensation heat exchange processes of the system is improved.
In some embodiments, the air conditioner further comprises a first throttling device 31, a seventh pipeline 107, an eighth pipeline 108 and a ninth pipeline 109, the fifth pipeline 105 and the sixth pipeline 106 are merged and then communicated to one end of the first throttling device 31 through the seventh pipeline 107, the other end of the first throttling device 31 is communicated to one end of the indoor first heat exchanger 41 through the eighth pipeline 108, and the other end of the indoor first heat exchanger 41 is communicated to the suction end or the exhaust end of the compressor 10 through the ninth pipeline 109. The indoor second heat exchanger and the indoor third heat exchanger can be effectively communicated with the indoor first heat exchanger through the seventh pipeline and the eighth pipeline, the indoor and outdoor refrigerant can be throttled and depressurized through the first throttling device, the indoor first heat exchanger can be communicated with the compressor through the ninth pipeline, the indoor first heat exchanger is communicated with the air suction end of the compressor in the refrigerating mode, and the indoor first heat exchanger is communicated with the air exhaust end of the compressor in the heating mode.
In some embodiments, the four-way valve 61 further comprises an E terminal E, an S terminal S, a C terminal C and a D terminal D, the E terminal E is communicated with the ninth pipeline 109, the S terminal S is communicated with the suction terminal of the compressor 10, the C terminal C is communicated with the first pipeline 101, the D terminal D is communicated with the discharge terminal of the compressor 10, and the first communication state of the four-way valve is: the E end E is communicated with the S end S, the C end C is communicated with the D end D, at the moment, indoor operation is in a refrigerating state, and the second communication state of the four-way valve is as follows: the E end E is communicated with the D end D, the S end S is communicated with the C end C, and at the moment, the indoor operation is in a heating state; the four-way valve 61 is switchable between the first communication state and the second communication state. This is a further preferred structural form of the present disclosure, and the indoor first heat exchanger, the outdoor first heat exchanger, and the compressor can be connected into an integrated system by the four-way valve, and can be switched to realize switching control between the cooling mode and the heating mode.
In some embodiments, the system further comprises a tenth pipeline 110 and an indoor second heat exchanger 42, wherein one end of the tenth pipeline 110 is communicated with the first pipeline 101 and penetrates into the gas-liquid separator 51 for heat exchange, and the other end is communicated to one end of the indoor second heat exchanger 42. This openly still through the setting of tenth pipeline and indoor second heat exchanger, can draw high temperature high pressure refrigerant in order to get into the gas-liquid separation in the gas branch and heat in the gas branch from the compressor exhaust under the refrigeration mode to improve gas-liquid separation's effect, and reach the tenth pipeline after the heat transfer to indoor second heat exchanger in, can carry out reheat effect to the indoor air after the indoor first heat exchanger refrigeration, in order to improve the comfort level of indoor air.
The main embodiment, as shown in fig. 1-2, in some embodiments, further includes an eleventh pipeline 111 and a second throttling device 32, the other end of the indoor second heat exchanger 42 is connected to the eighth pipeline 108 through the eleventh pipeline 111, and the second throttling device 32 is disposed on the eleventh pipeline 111. The structure in the main embodiment of the present disclosure is that the other end of the indoor second heat exchanger is connected to the eighth pipeline, that is, the position between the first throttling device and the indoor first heat exchanger (merging action), and after being merged, the merged indoor second heat exchanger enters the indoor first heat exchanger to be evaporated and absorb heat, and finally the merged indoor second heat exchanger returns to the suction end of the compressor.
3-4, an eleventh pipeline 111, a second throttling device 32, an indoor third heat exchanger 43 and a twelfth pipeline 112 are further included, the other end of the indoor second heat exchanger 42 is communicated to one end of the indoor third heat exchanger 43 through the eleventh pipeline 111, the eleventh pipeline 111 is provided with the second throttling device 32, and the other end of the indoor third heat exchanger 43 is communicated to the ninth pipeline 109 through the twelfth pipeline 112. The structure in the first alternative embodiment of the present disclosure is that the other end of the indoor second heat exchanger is connected to the second throttling device and the indoor third heat exchanger, so as to evaporate and absorb heat in the indoor third heat exchanger, join with the refrigerant after evaporating and absorbing heat from the indoor first heat exchanger, and finally return to the suction end of the compressor together. Can improve like this to indoor refrigeration evaporation heat transfer effect, realize refrigerating step by step, control as required, improve the comfort level to finally through reheat in order to improve the comfort level, realize the effect of intelligence refrigeration cooling.
An indoor third heat exchanger 43 is added behind the second throttling device, so that the refrigerant coming out of the second throttling device 32 is mixed with the refrigerant coming out of the indoor first heat exchanger 41 after heat exchange is completed in the indoor third heat exchanger 43, and the mixed refrigerant enters the suction port of the compressor through a four-way valve 61, thereby completing the whole cycle: other operating conditions and valve switching are consistent with the main embodiment.
Fig. 5-6 illustrate a second alternative embodiment of the present disclosure that differs from the main embodiment in that there is no reheat function, i.e., no exhaust gas is bypassed into the spiral coil, the system is more compact, and its mode of operation is consistent with the main embodiment.
In some embodiments, the portion of the pipe segment that the tenth pipe 110 penetrates into the gas-liquid separator 51 is not in communication with the fluid seal inside the gas-liquid separator 51; and/or, a part of the pipe section of the tenth pipe 110 penetrating into the gas-liquid separator 51 is a serpentine pipe section. This is this the preferred structural style of this disclosure's tenth pipeline, and it does not take place to leak in getting into the gas branch, only carries out the heat transfer effect, guarantees not to influence the heat transfer performance of the refrigerant in the gas branch, and snakelike bend section can increase heat transfer area, improves heat transfer effect.
In some embodiments, a first fan 81 is further included, and the first fan 81 can drive the indoor air flow to flow through the indoor first heat exchanger 41 and then flow through the indoor second heat exchanger 42, that is, the indoor second heat exchanger 42 is located at the downstream side of the indoor first heat exchanger 41 along the air flow direction. This is openly through the setting of first fan to indoor second heat exchanger sets up in the downstream side of the air current flow direction of indoor first heat exchanger, can make the room air earlier through indoor first heat exchanger refrigeration cooling, and the effect of reheating through indoor second heat exchanger can improve the comfort level of room air.
In some embodiments, when an indoor third heat exchanger 43 is further included, the first fan 81 can drive the indoor air flow to pass through the indoor first heat exchanger 41, the indoor third heat exchanger 43, and the indoor second heat exchanger 42 in sequence. This is the preferred structural style of this disclosed alternative embodiment one, still is provided with indoor third heat exchanger between indoor first heat exchanger and indoor second heat exchanger, can realize the process of cooling down and rising temperature step by step to the room air to control as required, improve indoor comfort level.
In some embodiments, a second fan 82 is also included:
the second fan 82 can drive the outdoor air flow to flow through the outdoor second heat exchanger 22 first and then flow through the outdoor first heat exchanger 21, that is, the outdoor first heat exchanger 21 is located on the downstream side of the outdoor second heat exchanger 22 along the air flow direction; and/or the second fan 82 can drive the outdoor air flow to flow through the outdoor third heat exchanger 23 first and then through the outdoor first heat exchanger 21, that is, the outdoor first heat exchanger 21 is located on the downstream side of the outdoor third heat exchanger 23 along the air flow direction. According to the outdoor heat exchanger, the second fan is arranged, the outdoor second heat exchanger is arranged on the upstream side of the airflow flowing direction of the outdoor first heat exchanger, so that indoor air can exchange heat through the outdoor second heat exchanger firstly and then through the outdoor first heat exchanger, and the temperature of the outdoor first heat exchanger is higher than that of the outdoor second heat exchanger, so that heat exchange of small temperature difference gradual temperature rise can be realized, and the heat exchange effect is improved; the outdoor third heat exchanger is arranged on the upstream side of the airflow flowing direction of the outdoor first heat exchanger, so that indoor air can exchange heat through the outdoor third heat exchanger firstly and then exchange heat through the outdoor first heat exchanger, and the heat exchange of small temperature difference gradual temperature rise can be realized due to the fact that the temperature of the outdoor first heat exchanger is higher than that of the outdoor third heat exchanger, and the heat exchange effect is improved.
In some embodiments, the outdoor second heat exchanger 22 and the outdoor third heat exchanger 23 are located in parallel along the airflow flowing direction, that is, the outdoor second heat exchanger 22 and the outdoor third heat exchanger 23 are located in a cross section perpendicular to the airflow flowing direction. The outdoor second heat exchanger and the outdoor third heat exchanger are in parallel positions in the airflow flowing direction, namely the outdoor second heat exchanger and the outdoor third heat exchanger are not distinguished by priority, and airflow can simultaneously flow through the outdoor second heat exchanger and the outdoor third heat exchanger to exchange heat.
The present disclosure also provides a method of controlling a variable load modulated air conditioning system as set forth in any of the preceding claims, comprising:
detecting the operation mode and the load working condition of the air conditioning system;
a judging step, namely judging the relation between the load working condition and the first preset value and the second preset value;
a control step, when the air conditioner is operated in a cooling mode: when the load is greater than or equal to a first preset value, the outdoor second heat exchanger 22 is controlled to be opened, and the outdoor third heat exchanger 23 is controlled to be closed; when the load is less than or equal to a second preset value, the outdoor second heat exchanger 22 is controlled to be closed, and the outdoor third heat exchanger 23 is controlled to be opened; when the load is smaller than the second preset value and smaller than the first preset value, the outdoor second heat exchanger 22 is controlled to be opened, and the outdoor third heat exchanger 23 is controlled to be opened; wherein the first preset value is more than or equal to the second preset value.
The air conditioning system shown in fig. 1 includes a compressor 10, an outdoor first heat exchanger 21, an outdoor second heat exchanger 22, an outdoor third heat exchanger 23, a first throttle device 31, a second throttle device 32, an indoor first heat exchanger 41, an indoor second heat exchanger 42, a gas-liquid separator 51, a first control valve 71, a second control valve 72, a first fan 81, a second fan 82, and the like.
The system circularly adopts non-azeotropic refrigerants, and the standard boiling points of the non-azeotropic refrigerants have certain difference, so that the non-azeotropic refrigerants can have different heat exchange characteristics from pure working media (or near-azeotropic working media) in the heat exchange process. In the evaporation process, the low boiling point working medium is firstly evaporated, so that the low boiling point working medium components in the gaseous refrigerant are continuously increased, and the concentration of the high boiling point components in the liquid refrigerant is gradually increased. Similarly, in the condensation process, the high boiling point component is firstly condensed, the concentration of the high boiling point component in the gaseous refrigerant is gradually reduced, and the concentration of the high boiling point component in the liquid refrigerant is gradually increased. Therefore, the system cycle makes full use of the above characteristics of the non-azeotropic working medium, and combines the component separation technology to provide a new system cycle, and the specific implementation mode is as follows:
in some embodiments, when further comprising a first control valve 71 and a second control valve 72:
in the control step, when the load is larger than or equal to a first preset value, the first control valve 71 is opened, and the second control valve 72 is closed; when the load is less than or equal to a second preset value, closing the first control valve 71 and opening the second control valve 72; when the second preset value < load < first preset value, the first control valve 71 is opened, and the second control valve 72 is opened.
1. In the refrigeration mode of fig. 1, the adjustment of the system load is realized by switching the valves. Generally, the volume refrigerating capacity of the low boiling point is large, the volume refrigerating capacity of the high boiling point is small, the component concentrations of refrigerant with high boiling point and low boiling point in the system are adjusted under the same compressor displacement and frequency, the adjustment of system load is achieved, meanwhile, the non-azeotropic capacity adjusting characteristic is coupled with the compressor frequency conversion technology, the system capacity adjustment under wider working conditions is achieved, therefore, the system can run near the optimal state point under different working conditions, meanwhile, in order to fully utilize the temperature slippage characteristic of the non-azeotropic working medium, the indoor first heat exchanger 41 is suitable for selecting and using multiple rows of heat exchangers, and other heat exchangers are similar. The specific implementation mode is as follows:
a. under the refrigeration working condition, when the load is large, the concentration of the high-pressure component (low boiling point) is increased, at the moment, the second control valve 72 is closed, and the first control valve 71 is opened.
The high-temperature and high-pressure refrigerant discharged from the compressor 10 is divided into two paths, one path of the refrigerant enters the outdoor first heat exchanger 21, is condensed into a vapor-liquid two-phase state, and then enters the gas-liquid separator 51 (the gas-liquid separator stores a certain amount of mixed refrigerant), at this time, the liquid phase in the gas-liquid separator mainly contains low-pressure components (high boiling point), and the gas phase mainly contains high-pressure components (low boiling point). As the first control valve 71 (preferably, two-way valve) is opened and the second control valve 72 (preferably, two-way valve) is closed, the gaseous refrigerant with the high-pressure component (low-boiling point) component being abundant enters the outdoor second heat exchanger 22 to be condensed into a liquid state, and then is throttled and depressurized through the first throttling means 31; the other path of refrigerant from the compressor enters a built-in spiral coil in the gas-liquid separator 51, and the liquid refrigerant in the gas-liquid separator is heated, so that the low-boiling-point refrigerant in the liquid refrigerant is volatilized, and the separation purity is improved. The refrigerant that comes out from spiral coil gets into indoor second heat exchanger 42 heat transfer, improves indoor air supply temperature, improves air supply travelling comfort, after second throttling arrangement 32 throttle step-down afterwards, mixes with the main road refrigerant that comes out from first throttling arrangement 31, and the refrigerant after the mixture gets into indoor first heat exchanger 41 heat transfer, then gets into the induction port of compressor through four-way valve 61, is discharged after the completion of the compression to accomplish whole refrigeration cycle. In this mode, the system has a large amount of circulating low boiling point components, a large capacity refrigerating capacity and a large load.
b. In the refrigeration condition, when the load is small, the concentration of the low-pressure component (high boiling point) is increased, and at this time, the second control valve 72 is opened and the first control valve 71 is closed.
The high-temperature and high-pressure refrigerant discharged from the compressor 10 is divided into two paths, one of which enters the outdoor first heat exchanger 21, is condensed into a gas-liquid two-phase state, and then enters the gas-liquid separator 51 (where a certain amount of refrigerant is stored), where the liquid phase is mainly low-pressure (high-boiling point) refrigerant and the vapor phase is mainly high-pressure (low-boiling point) refrigerant. As the second control valve 72 is opened, the first control valve 71 is closed, and the liquid refrigerant mainly containing low-pressure (high-boiling point) components enters the outdoor third heat exchanger 23 for further supercooling, and then is throttled and depressurized by the first throttling device 31; the other path of refrigerant from the compressor enters a built-in spiral coil in the gas-liquid separator 51, and the liquid refrigerant in the gas-liquid separator is heated to volatilize high-pressure components (low boiling point) in the liquid refrigerant, so that the concentration of high-boiling point components in the liquid refrigerant in the gas-liquid separator is increased. The refrigerant coming out of the spiral coil enters the indoor second heat exchanger 42 for heat exchange, then is throttled and depressurized by the second throttling device 32, is mixed with the refrigerant mainly with a high boiling point coming out of the first throttling device 31, then enters the indoor first heat exchanger 41 for heat exchange, passes through the four-way valve 61 after the heat exchange is finished, enters an air suction port of the compressor, is compressed and discharged after the completion, and therefore the whole refrigeration cycle is completed. In this mode, the high boiling point components circulating in the system are more, the volume refrigerating capacity is smaller, and the load is smaller.
c. In the cooling mode, when the compressor is operating at a normal ratio, both the first control valve 71 and the second control valve 72 are opened.
High-temperature and high-pressure refrigerant gas discharged by the compressor 10 is divided into two paths, one path of the high-temperature and high-pressure refrigerant gas directly enters the outdoor first heat exchanger 21 for heat exchange, the high-temperature and high-pressure refrigerant gas is condensed into a gas-liquid two-phase state and then enters the gas-liquid separator 51, the liquid phase in the gas-liquid separator mainly comprises a low-pressure component (high boiling point) and the gas phase mainly comprises a high-pressure component (low boiling point), and the refrigerant with a large proportion of gaseous high-pressure component (low boiling point) enters the outdoor second heat exchanger 22 for heat exchange and is condensed into a liquid state; the refrigerant with a large liquid low-pressure component (high boiling point) ratio enters the outdoor third heat exchanger 23 to be further subcooled, then the two paths of refrigerants are mixed, and the throttling and pressure reduction are carried out through the first throttling device 31; and the other path of refrigerant discharged from the compressor enters a spiral coil arranged in the gas-liquid separator 51, the liquid refrigerant in the gas-liquid separator 51 is heated to improve the separation purity, then the refrigerant sequentially passes through the indoor second heat exchanger 42 and the second throttling device 32 and is finally mixed with the refrigerant discharged from the first throttling device 31, the mixed refrigerant enters the indoor first heat exchanger 41 for heat exchange, enters an air suction port of the compressor through the four-way valve 61 after the heat exchange is finished, is compressed and discharged, and the whole refrigeration cycle is finished.
In some embodiments, the detecting step can also detect the outdoor ambient temperature T;
the judging step is to judge the relation between the T outside and a third preset temperature and a fourth preset temperature;
in the control step, when the third preset temperature is not less than T and not more than the fourth preset temperature, the outdoor second heat exchanger 22 and the outdoor third heat exchanger 23 are controlled to be communicated; and when Tout is less than a third preset temperature, controlling the outdoor second heat exchanger 22 and the outdoor third heat exchanger 23 to be alternately communicated.
In some embodiments, when further comprising a first control valve 71 and a second control valve 72:
in the control step, when the third preset temperature is not more than T and not more than the fourth preset temperature, the first control valve 71 and the second control valve 72 are both controlled to be opened; and when Tout < the third preset temperature, controlling the first control valve 71 and the second control valve 72 to be opened alternately.
2. When the heating working condition is operated (figure 2), the system can realize alternate defrosting and defrosting of the outdoor heat exchanger through switching of the valve without stopping, thereby ensuring normal indoor heating. Meanwhile, the temperature slippage characteristic of the non-azeotropic working medium is fully utilized, because the non-azeotropic working medium gradually slips to the dew point temperature from the bubble point temperature in the heat exchange process in the evaporator, the temperature is gradually increased, and the slippage temperature of the non-azeotropic working medium is higher, the phenomenon is more obvious. Therefore, in the cold and dry season in the north, the dry bulb temperature and the dew point temperature of the outdoor air are different greatly, and the system can give full advantage. By the control program, during heating operation, the evaporating temperature of the outdoor second heat exchanger 22 and the outdoor third heat exchanger 23 is lower than the dew-point temperature of the outdoor environment, and the evaporating temperature of the outdoor second heat exchanger 22 is higher than the dew-point temperature of the outdoor environment but lower than the dry bulb temperature of the outdoor environment. Therefore, when the outdoor first heat exchanger 21 is operated in a severe working condition and a refrigerating mode, frosting can not occur, frosting can only occur on the outdoor second heat exchanger 22 and the outdoor third heat exchanger 23, and then heating operation and defrosting are carried out simultaneously through switching of the valves, and continuity and stability of system operation and comfort of a heating environment are improved. The specific operation mode is as follows:
a. in the heating operation under the normal working condition (the outdoor heat exchanger does not frost), the first control valve 71 and the second control valve 72 are both opened, and the second throttling device 32 is closed;
at the moment, high-temperature and high-pressure exhaust of the compressor enters the indoor first heat exchanger 41 through the four-way valve 61, exchanges heat with indoor air, is condensed into liquid after heat exchange, then enters the outdoor second heat exchanger 22 and the outdoor third heat exchanger 23 respectively after being throttled and depressurized through the first throttling device 31 to exchange heat, absorbs heat of an outdoor environment, then passes through the gas-liquid separator 51 (the gas-liquid separator 51 is equivalent to a liquid storage tank), enters the outdoor first heat exchanger 21, enters an air suction port of the compressor through the four-way valve after heat exchange is finished, is compressed and discharged, and therefore the whole heating cycle is finished.
b. When heating is performed under severe conditions (the outdoor heat exchanger may frost), the first control valve 71 and the second control valve 72 are alternately opened, and when the heating is performed, it is ensured that only one valve is opened and the second throttling device 32 is closed.
At this time, the high-temperature and high-pressure exhaust gas of the compressor is subjected to heat exchange by the indoor first heat exchanger 41, and then is throttled and depressurized by the first throttling device 31. At this time, the first control valve 71 is opened and the second control valve 72 is closed. At this time, because the environment temperature of the outdoor side is lower, the evaporation temperature is also lower and is lower than the dew point temperature of the outdoor environment, the outdoor heat exchanger is easy to frost, the refrigerant frosts after heat exchange through the outdoor second heat exchanger 22, but the non-azeotropic working medium has the temperature slip characteristic, the temperature of the refrigerant after heat exchange in the outdoor second heat exchanger 22 is increased, and through the early-stage system matching and control, the temperature of the refrigerant coming out of the outdoor second heat exchanger 22 is increased and is higher than the dew point temperature of the outdoor environment but is lower than the dry bulb temperature of the outdoor environment; then, the refrigerant passes through the gas-liquid separator 51 (which is equivalent to only one liquid storage tank), enters the outdoor first heat exchanger 21 for heat exchange, enters the air suction port of the compressor through the four-way valve 61 after the heat exchange is finished, is compressed and discharged, and then the whole heating cycle is finished. As the system is continuously operated, frost on the outdoor second heat exchanger 22 becomes thicker and thicker, and heat exchange becomes worse. At this time, the first control valve 71 is closed, the second control valve 72 is opened, and the outdoor third heat exchanger 23 operates in place of the outdoor second heat exchanger 22, and the system operation is performed in the same manner as described above. At this time, the defrosting process is performed on the outdoor second heat exchanger 22. When the defrosting treatment of the outdoor second heat exchanger 22 is completed and the frosting heat exchange of the outdoor third heat exchanger 23 is poor, the control valves are switched, so that the first control valve 71 is opened and the second control valve 72 is closed, and the process is repeated in this way, and only one outdoor second heat exchanger 22 and one outdoor third heat exchanger 23 in the system participate in circulation each time, so that the system does not stop during heating operation and continuously defrosts and defrosts. And the stability of the system operation is ensured.
In conclusion, the system innovatively applies the non-azeotropic refrigerant to the cooling and heating unit, and fully utilizes the capacity regulating property (refrigeration) and the temperature slip property of the non-azeotropic working medium. The system can run efficiently and stably under different working conditions.
During refrigeration operation, the capacity of the non-azeotropic working medium is coupled with the frequency conversion technology of the compressor, so that the system can efficiently operate under a wider working condition. The condensation side adopts a component separation mode, and the change of the operation concentration component of the refrigerant in the system (the change of the concentration component of the refrigerant in the system and the corresponding change of the volume refrigerating capacity) is realized by switching the valve, so that the adjustment of the system capacity is realized. Through the component separation mode of adoption, alleviate the heat transfer "aggravation" effect of refrigerant in the heat transfer process, promote the heat exchange efficiency of system. Meanwhile, a spiral coil is arranged in the gas-liquid separator 51, and high-temperature exhaust gas is used for heating liquid in the gas-liquid separator, so that a low-boiling-point working medium in a liquid phase is volatilized, and the separation purity is improved. The indoor second heat exchanger 42 heats the cooled and dehumidified air, so that the temperature of the outlet air is not too low, and the comfort of the indoor environment temperature is improved.
When the heat exchanger is used for heating, the temperature slip characteristic of the non-azeotropic working medium is fully utilized, a small part of the area of the outdoor heat exchanger is sacrificed, and the frosting prevention of the main body of the heat exchanger is ensured. Therefore, the system can run stably and continuously, the machine does not need to be stopped when heating and defrosting are carried out, and the comfort of the indoor environment is ensured.
The above description is only exemplary of the present disclosure and should not be taken as limiting the disclosure, as any modification, equivalent replacement, or improvement made within the spirit and principle of the present disclosure should be included in the scope of the present disclosure. The foregoing is only a preferred embodiment of the present disclosure, and it should be noted that, for those skilled in the art, several modifications and variations can be made without departing from the technical principle of the present disclosure, and these modifications and variations should also be regarded as the protection scope of the present disclosure.

Claims (13)

1. A variable load air conditioning system is characterized in that: the method comprises the following steps:
the air-conditioning system comprises a compressor (10), an outdoor first heat exchanger (21), an outdoor second heat exchanger (22), an outdoor third heat exchanger (23), an indoor first heat exchanger (41) and a gas-liquid separator (51), wherein the gas-liquid separator (51) comprises a first end (51 a), a second end (51 b) and a third end (51 c), the air-conditioning system comprises a first boiling point refrigerant and a second boiling point refrigerant, the boiling point of the first boiling point refrigerant is less than that of the second boiling point refrigerant, one end of the outdoor first heat exchanger (21) can be communicated to a gas discharge end or a gas suction end of the compressor (10), and the other end of the outdoor first heat exchanger can be communicated to the first end (51 a) of the gas-liquid separator (51);
the second end (51 b) is a gas end, the gas separated from the gas-liquid separator (51) can be communicated with one end of the outdoor second heat exchanger (22) through the second end (51 b), the third end (51 c) is a liquid end, and the liquid separated from the gas-liquid separator (51) can be communicated with one end of the outdoor third heat exchanger (23) through the third end (51 c);
the other end of the outdoor second heat exchanger (22) and the other end of the outdoor third heat exchanger (23) can be communicated with one end of the indoor first heat exchanger (41) after being mixed, and the other end of the indoor first heat exchanger (41) can be communicated to a suction end or a discharge end of the compressor (10);
when the load is larger than or equal to a first preset value, the outdoor second heat exchanger (22) can be controlled to be opened, and the outdoor third heat exchanger (23) can be controlled to be closed; when the load is less than or equal to a second preset value, the outdoor second heat exchanger (22) can be controlled to be closed, the outdoor third heat exchanger (23) can be controlled to be opened, and the first preset value is greater than or equal to the second preset value;
one end of the outdoor first heat exchanger (21) is communicated to a discharge end or a suction end of the compressor (10) through a first pipeline (101), the other end of the outdoor first heat exchanger is communicated to the first end (51 a) of the gas-liquid separator (51) through a second pipeline (102), the second end (51 b) of the gas-liquid separator (51) is communicated with one end of the outdoor second heat exchanger (22) through a third pipeline (103), and the third end (51 c) is communicated with one end of the outdoor third heat exchanger (23) through a fourth pipeline (104);
the other end of the outdoor second heat exchanger (22) is communicated to one end of a fifth pipeline (105), the other end of the outdoor third heat exchanger (23) is communicated to one end of a sixth pipeline (106), the other end of the fifth pipeline (105) is converged with the other end of the sixth pipeline (106), a first control valve (71) is arranged on the fifth pipeline (105), and a second control valve (72) is arranged on the sixth pipeline (106);
when the load is larger than or equal to a first preset value, the first control valve (71) is opened in a mode of controlling the outdoor second heat exchanger (22) to be opened, and the second control valve (72) is closed in a mode of controlling the outdoor third heat exchanger (23) to be closed; when the load is less than or equal to a second preset value, the mode that the outdoor second heat exchanger (22) is controlled to be closed is to close the first control valve (71), and the mode that the outdoor third heat exchanger (23) is controlled to be opened is to open the second control valve (72);
the system is characterized by further comprising a first throttling device (31), a seventh pipeline (107), an eighth pipeline (108) and a ninth pipeline (109), wherein the fifth pipeline (105) and the sixth pipeline (106) are converged and then communicated to one end of the first throttling device (31) through the seventh pipeline (107), the other end of the first throttling device (31) is communicated to one end of the indoor first heat exchanger (41) through the eighth pipeline (108), and the other end of the indoor first heat exchanger (41) is communicated to the suction end or the exhaust end of the compressor (10) through the ninth pipeline (109);
the heat exchanger further comprises a tenth pipeline (110) and an indoor second heat exchanger (42), wherein one end of the tenth pipeline (110) is communicated with the first pipeline (101) and then penetrates into the gas-liquid separator (51) for heat exchange, and the other end of the tenth pipeline is communicated to one end of the indoor second heat exchanger (42).
2. The variable load modulating air conditioning system of claim 1 wherein:
the first end (51 a) and the third end (51 c) are both located at the bottom of the gas-liquid separator (51), and the second end (51 b) is located above half the height of the gas-liquid separator (51).
3. The variable load modulated air conditioning system of claim 1, wherein:
the four-way valve further comprises a four-way valve (61), the four-way valve comprises an E end (E), an S end (S), a C end (C) and a D end (D), the E end (E) is communicated with the ninth pipeline (109), the S end (S) is communicated with the air suction end of the compressor (10), the C end (C) is communicated with the first pipeline (101), the D end (D) is communicated with the air exhaust end of the compressor (10), and the first communication state of the four-way valve is as follows: the E end (E) is communicated with the S end (S), the C end (C) is communicated with the D end (D), at the moment, the indoor operation is in a refrigerating state, and the second communication state of the four-way valve is as follows: the end E is communicated with the end D, the end S is communicated with the end C, and the indoor operation is in a heating state; the four-way valve (61) can be switched between the first communication state and the second communication state.
4. The variable load modulated air conditioning system of claim 1, wherein:
the other end of the indoor second heat exchanger (42) is communicated to the eighth pipeline (108) through the eleventh pipeline (111), and the eleventh pipeline (111) is provided with a second throttling device (32);
or the heat exchanger further comprises an eleventh pipeline (111), a second throttling device (32), an indoor third heat exchanger (43) and a twelfth pipeline (112), the other end of the indoor second heat exchanger (42) is communicated to one end of the indoor third heat exchanger (43) through the eleventh pipeline (111), the eleventh pipeline (111) is provided with the second throttling device (32), and the other end of the indoor third heat exchanger (43) is communicated to the ninth pipeline (109) through the twelfth pipeline (112).
5. The variable load modulated air conditioning system of claim 1, wherein:
the part of the pipe section of the tenth pipeline (110) penetrating into the gas-liquid separator (51) is not communicated with the fluid seal inside the gas-liquid separator (51); and/or the part of the pipe section penetrating into the gas-liquid separator (51) from the tenth pipeline (110) is a serpentine pipe section.
6. A variable load adjustment air conditioning system according to any one of claims 1 to 5, characterized in that:
the air conditioner further comprises a first fan (81), wherein the first fan (81) can drive the indoor air flow to firstly flow through the indoor first heat exchanger (41) and then flow through the indoor second heat exchanger (42), namely the indoor second heat exchanger (42) is positioned on the downstream side of the indoor first heat exchanger (41) along the air flow direction.
7. The variable load regulated air conditioning system of claim 6, wherein:
when an indoor third heat exchanger (43) is further included, the first fan (81) can drive indoor airflow to sequentially pass through the indoor first heat exchanger (41), the indoor third heat exchanger (43) and the indoor second heat exchanger (42).
8. A variable load modulated air conditioning system as claimed in any one of claims 1 to 5, wherein:
further comprising a second fan (82):
the second fan (82) can drive outdoor airflow to firstly flow through the outdoor second heat exchanger (22) and then flow through the outdoor first heat exchanger (21), namely the outdoor first heat exchanger (21) is positioned on the downstream side of the outdoor second heat exchanger (22) along the airflow flowing direction; and/or the second fan (82) can drive the outdoor air flow to flow through the outdoor third heat exchanger (23) firstly and then flow through the outdoor first heat exchanger (21), namely the outdoor first heat exchanger (21) is positioned at the downstream side of the outdoor third heat exchanger (23) along the air flow direction.
9. The variable capacity modulated air conditioning system of claim 8, wherein:
the outdoor second heat exchanger (22) and the outdoor third heat exchanger (23) are located in parallel along the airflow flowing direction, namely, the outdoor second heat exchanger (22) and the outdoor third heat exchanger (23) are located in a section perpendicular to the airflow flowing direction.
10. A control method of a variable load adjustment air conditioning system according to any one of claims 1 to 9, characterized in that: the method comprises the following steps:
detecting the operation mode and the load working condition of the air conditioning system;
a judging step, namely judging the relation between the load working condition and the first preset value and the second preset value;
a control step, when the air conditioner is operated in a cooling mode: when the load is larger than or equal to a first preset value, the outdoor second heat exchanger (22) is controlled to be opened, and the outdoor third heat exchanger (23) is controlled to be closed; when the load is less than or equal to a second preset value, the outdoor second heat exchanger (22) is controlled to be closed, and the outdoor third heat exchanger (23) is controlled to be opened; when the load is smaller than the second preset value and smaller than the first preset value, the outdoor second heat exchanger (22) is controlled to be opened, and the outdoor third heat exchanger (23) is controlled to be opened; wherein the first preset value is more than or equal to the second preset value.
11. The control method according to claim 10, characterized in that:
when further comprising a first control valve (71) and a second control valve (72):
in the control step, when the load is larger than or equal to a first preset value, the first control valve (71) is opened, and the second control valve (72) is closed; when the load is less than or equal to a second preset value, closing the first control valve (71) and opening the second control valve (72); -opening said first control valve (71), and-opening said second control valve (72), when the second preset value < load < first preset value.
12. The control method according to claim 10, characterized in that:
the detecting step can also detect the outdoor ambient temperature T Outer cover ；
The judging step of judging T Outer cover A relationship with a third preset temperature and a fourth preset temperature;
the control step is that when the third preset temperature is less than or equal to T Outer cover When the temperature is less than or equal to a fourth preset temperature, controlling the outdoor second heat exchanger (22) and the outdoor third heat exchanger (23) to be communicated; when T is Outer cover And when the temperature is lower than the third preset temperature, controlling the outdoor second heat exchanger (22) and the outdoor third heat exchanger (23) to be alternately communicated.
13. The control method according to claim 12, characterized in that:
when further comprising a first control valve (71) and a second control valve (72):
in the control step, when the third preset temperature is less than or equal to T Outer cover When the temperature is less than or equal to a fourth preset temperature, controlling the first control valve (71) and the second control valve (72) to be opened; when T is Outer cover And when the temperature is lower than a third preset temperature, controlling the first control valve (71) and the second control valve (72) to be opened alternately.
CN202111265937.8A 2021-10-28 2021-10-28 Variable-load adjusting air conditioning system and control method thereof Active CN113865012B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202111265937.8A CN113865012B (en) 2021-10-28 2021-10-28 Variable-load adjusting air conditioning system and control method thereof

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202111265937.8A CN113865012B (en) 2021-10-28 2021-10-28 Variable-load adjusting air conditioning system and control method thereof

Publications (2)

Publication Number Publication Date
CN113865012A CN113865012A (en) 2021-12-31
CN113865012B true CN113865012B (en) 2023-01-17

Family

ID=78985771

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202111265937.8A Active CN113865012B (en) 2021-10-28 2021-10-28 Variable-load adjusting air conditioning system and control method thereof

Country Status (1)

Country Link
CN (1) CN113865012B (en)

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3487710B2 (en) * 1996-02-28 2004-01-19 松下電器産業株式会社 Refrigeration cycle operation method and air conditioner using it
JP5242434B2 (en) * 2009-01-30 2013-07-24 パナソニック株式会社 Liquid circulation heating system
CN106524399A (en) * 2016-10-31 2017-03-22 芜湖美智空调设备有限公司 Air conditioner defrosting device, air conditioner defrosting control method and system and air conditioner
CN108844249B (en) * 2018-04-02 2020-10-09 合肥华凌股份有限公司 Supercooling circulation system control method, supercooling circulation system and refrigerator
CN110762648A (en) * 2019-10-18 2020-02-07 珠海格力电器股份有限公司 Heat recovery fresh air dehumidifier
CN113324363A (en) * 2020-02-12 2021-08-31 合肥华凌股份有限公司 Refrigeration system, refrigeration equipment and control method of refrigeration equipment

Also Published As

Publication number Publication date
CN113865012A (en) 2021-12-31

Similar Documents

Publication Publication Date Title
CN211739592U (en) Air conditioning system capable of continuously heating
CN206919454U (en) Heat exchanger and air-conditioning device for air-conditioning device
KR100447203B1 (en) Multi-type air conditioner for cooling/heating the same time and method for controlling the same
WO2013145006A1 (en) Air conditioning device
CN110332635B (en) Double-stage compression multi-air-supplementing refrigeration heat pump system, control method and air conditioner
CN107763774A (en) Air conditioner cooling cycle system and air conditioner
WO2015158138A1 (en) Refrigeration device
KR20030095614A (en) Multi-type air conditioner for cooling/heating the same time and method for controlling the same
JP2012193897A (en) Refrigeration cycle device
KR20070007771A (en) Freezing apparatus
CN113154522B (en) Multi-connected air conditioner system and defrosting control method
CN109654764A (en) A kind of two-stage enthalpy increasing system and its defrosting control method
US20210010733A1 (en) Air conditioning system and control method therefor
JP4179595B2 (en) Air conditioner
CN206556168U (en) Energy-efficient air energy two-shipper heat pump type air conditioning system
KR20120053381A (en) Refrigerant cycle apparatus
CN113865012B (en) Variable-load adjusting air conditioning system and control method thereof
CN107499089A (en) A kind of electric automobile heat-pump air-conditioning system and its method of work
CN111059732A (en) Air conditioner and control method thereof
CN113865013B (en) Variable-load adjusting air conditioning system and control method thereof
CN215930176U (en) Refrigerating system
CN113587469B (en) Control device and method of temperature control system and temperature control system
CN213089945U (en) Air conditioner
CN105972864A (en) Non-azeotropic mixed working medium heat pump air-conditioning system with concentration adjustable
CN205448416U (en) Air conditioner of quick -witted steam defrosting in adoption air conditioning

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
GR01 Patent grant
GR01 Patent grant